JP2008261615A - Heat exchanger, heat exchange device, refrigerator and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger, a refrigerator and an air conditioner, easy in manufacture, capable of preventing leakage of a refrigerant, capable of reducing ventilation resistance, and superior in clogging yield strength such as dust. <P>SOLUTION: This heat exchanger has a laminated body 22 laminated by arranging a clearance by bending one flat heat transfer tube 21 in a meandering shape, and an air duct formed of the whole clearance. The laminated body 22 is arranged in a plurality in the ventilation direction. A pair of adjacent laminated bodies 22 are connected by the flat heat transfer tube 21 on one bending side of one laminated body 22 and the other bending side of the other laminated body 22. A flat heat transfer tube 21 part of one laminated body 22 and a clearance part of the other laminated body 22 are oppositely arranged. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a heat exchanger, a refrigerator, and an air conditioner.

  As a conventional heat exchanger, a corrugated fin laminated between flat tubes is known (Patent Document 1).

Japanese Patent Laying-Open No. 2005-90760 (FIG. 1)

  In the conventional plate fin tube type and corrugated fin type heat exchangers, firstly, the manufacturing process of laminating fins (corrugated fins, etc.) between heat transfer tubes (flat tubes, etc.) is complicated, and workability is poor. There was a problem. Second, when using a plurality of heat exchangers, the heat transfer tubes of each heat exchanger are connected using U-bends or headers, which causes a problem that the refrigerant leaks. Thirdly, the use of fins has a problem in that ventilation resistance increases and a powerful blower is required. Fourth, since the fins have fine meshes, there is a problem that dust or oil adheres and clogging is likely to occur.

  The present invention has been made in order to solve the above-described problems. In addition to being easy to manufacture, the present invention can prevent leakage of refrigerant, has low ventilation resistance, and has excellent resistance to clogging such as dust. An object is to provide an exchange device), a refrigerator, and an air conditioner.

A heat exchanger according to the present invention includes a laminated body in which a flat heat transfer tube is bent in a meandering manner and provided with a gap, and an air passage formed with the whole gap, and a plurality of laminated bodies are provided in the ventilation direction. The pair of adjacent stacked bodies are arranged such that one folded side of one stacked body and the other folded side of the other stacked body are connected by a flat heat transfer tube, and the flat heat transfer tube portion of the one stacked body The other laminated body is disposed so as to face the gap portion.
The refrigerator according to the present invention includes a refrigeration cycle in which a compressor, a condenser, a throttling means, and a cooler are sequentially connected, and the heat exchanger is used for the condenser.
Furthermore, the air conditioner according to the present invention includes a refrigeration cycle in which a compressor, a condenser, a throttle means, and a cooler are sequentially connected, and the above heat exchanger is used for the condenser.

The heat exchanger according to the present invention can be easily manufactured by simply bending a flat heat transfer tube into a meandering shape, so that processing work for parts such as fins is not required, and the manufacturing cost can be greatly reduced. it can. In addition, since a plurality of laminated bodies (heat exchangers) are formed by a single flat heat transfer tube, it is not necessary to use a U-bend or a header to connect the flat heat transfer tubes, thereby preventing refrigerant leakage. it can.
Moreover, since the air passage is formed in the entire gap between the adjacent flat heat transfer tubes, the cross-sectional area of the air passage is increased. As a result, the ventilation resistance is reduced, and the power of the blower can be reduced.
Furthermore, since the air passage is formed in the entire gap, the cross-sectional area of the air passage is increased. As a result, foreign matters such as dust are not easily clogged, and heat transfer performance can be maintained for many years. In particular, heat transfer performance can be maintained for many years, even when heat exchangers are placed in places (such as machine rooms) where dust adheres easily, such as the lower back of refrigerators, and are highly reliable. The refrigerator can be supplied.

Embodiment 1 FIG.
A preferred embodiment 1 of the present invention will be described below with reference to the accompanying drawings.
FIG. 1 is a front view showing the refrigerator according to the first embodiment. Moreover, FIG. 2 is a rear view which shows the state which removed the machine room cover of the refrigerator which concerns on this Embodiment 1. FIG. Furthermore, FIG. 3 is a circuit diagram showing the configuration of the refrigerant circuit of the refrigerator according to the first embodiment. As shown in FIGS. 1 and 2, 1 is a refrigerated room for refrigerated storage of food, 2 is an ice making room for creating ice, 3 is a switching room that can be switched to either a refrigerated room or an ice making room, and 4 is a vegetable. A vegetable room 5 for refrigerated storage, 5 a freezer room for storing frozen foods, 6 a machine room provided on the lower back of the main body, and 7 a blower provided in the machine room 6.

  Further, as shown in FIG. 3, 11 is a compressor, 13 is a first condenser, 14 is a second condenser, 15 is a third condenser, 16 is a capillary tube as a throttle means, and 17 is a cooler. , 18 are low-pressure accumulators. The first condenser 13, the second condenser 14, the third condenser 15, and the cooler 17 constitute the heat exchanger according to the present embodiment. The compressor 11, the first condenser 13, the second condenser 14, the third condenser 15, the capillary tube 16, the cooler 17, and the low-pressure accumulator 18 are sequentially connected by a pipe to constitute a refrigeration cycle. . The refrigerant circuit uses natural refrigerant R600a (isobutane).

  As shown in FIGS. 1 and 2, the first condenser 13 is installed in the machine room 6, and is cooled with air of about room temperature (30 ° C.) supplied from the blower 7. The second condenser 14 is installed between the outer box (steel plate) and the heat insulating material (urethane) on the side wall of the refrigerator main body. The third condenser 15 is embedded in the opening of the refrigerator main body, and has a function of preventing dew around the door due to leakage of cold heat when the door is opened and closed. It has heat dissipation points.

  FIG. 4 is a perspective view showing a detailed structure of the first condenser 13. As shown in the figure, the first condenser 13 includes a laminated body 22 in which one flat heat transfer tube 21 is bent in a meandering manner to provide a gap, and an air passage 23 formed in the entire gap. ing.

The first condenser 13 bends one flat heat transfer tube 21 in a meandering manner from the bottom surface toward the top surface, and stacks a plurality of flat heat transfer tubes 21 upward to form a first-layer laminated body 22a. Is forming. In the uppermost stage, the flat heat transfer tubes 21 are bent and moved in the horizontal direction (ventilation direction), bent again from the top surface to the bottom surface, and a plurality of flat heat transfer tubes 21 are stacked downward, and the second row of stacked bodies 22b is formed. Forming. Furthermore, it is bent again in the horizontal direction (ventilation direction) at the lowest level, and a plurality of levels of flat heat transfer tubes 21 are stacked upward to form a third-layer stacked body 22c. The capacity of the heat exchanger can be easily adjusted by increasing the number of times of bending in the number of stages (stacking direction) or increasing the number of times of bending in the row direction (ventilation direction).
Inside the flat heat transfer tube 21, partition walls are provided at equal intervals and partitioned into a plurality of refrigerant flow paths. Further, aluminum (A1050) is used as the material of the flat heat transfer tube 21.
Here, by arranging a plurality of the stacked bodies 22 in the row direction (ventilation direction), a desired capacity of the heat exchanger can be secured while suppressing the number of stacked layers of the stacked bodies 22, and a narrow place in the height direction. In addition, the heat exchanger can be installed.
Moreover, since the several laminated body 22 is comprised from the one flat heat exchanger tube 21, while being able to reduce a number of parts significantly, a heat exchanger can be comprised only by bending the one flat heat exchanger tube 21, Processing work is facilitated, and manufacturing costs can be greatly reduced.

  Further, in the first embodiment, the bent portion on the upper back side of the laminated body 22a having substantially the same height and the bent portion on the upper front side of the laminated body 22b are connected substantially horizontally by the flat heat transfer tube 21. Yes. Further, the bent part on the lower back side of the laminated body 22b having substantially the same height and the bent part on the lower front side of the laminated body 22c are connected substantially horizontally by the flat heat transfer tube 21. For this reason, each laminated body 22 can be connected without the unevenness | corrugation to an up-down direction, and can manufacture the 1st condenser 13 more compactly.

  The stacked body 22b in the second row is shifted in the vertical upward direction (upward direction of the stack) by 0.5 steps with respect to the stacked body 22a in the first row. Similarly, the stacked body 22c in the third row is arranged so as to be shifted in the vertical downward direction (downward direction of the stack) by 0.5 steps with respect to the stacked body 22b in the second row. With this arrangement, the gap portion of the stacked body 22a in the first row and the flat heat transfer tube portion of the stacked body 22b in the second row face each other. In addition, the gap portion of the stacked body 22b in the second row and the flat heat transfer tube portion of the stacked body 22c in the third row face each other.

  In general, when a plurality of laminated bodies 22 are arranged and blown from one side, a large amount of wind hits the near-side laminated body 22a, but the far-side laminated bodies 22b and 22c are obstructed by the near-side laminated body 22a. The wind does not get enough, and the overall heat dissipation efficiency is poor. On the other hand, according to the first embodiment, the gap portions of the stacked bodies 22 in the respective rows and the flat heat transfer tube portions of the stacked bodies 22 are alternated. It passes through the gap portion (air passage 23) of the laminated body 22a and hits the flat heat transfer tube portion of the laminated body 22b in the second row without an obstacle. Further, the wind that hits the flat heat transfer tube portion of the second-row laminated body 22b is divided into two with low resistance because the heat transfer tube is flat, and the gap portion (air passage 23) of the second-row laminated body 22b. And hits the flat heat transfer tube portion of the laminated body 22c in the third row without any obstacle. As a result, the overall heat dissipation efficiency is improved.

  FIG. 5 is a perspective view showing a schematic configuration of the connection member 24. The connection member 24 connects the tubular pipe from the compressor 11 and the first condenser 13. The connection member 24 is made of aluminum, and expands one end of a circular connection pipe and crushes and deforms it into a flat shape to match the shape of the flat heat transfer tube 21. The end of the flat heat transfer tube 21 and the flat end of the connecting member 24 are connected by brazing or welding. In this way, the tubular pipe from the compressor 11 having a greatly different shape and the flat flat heat transfer tube 21 can be connected very simply by the connecting member 24, and the efficiency of the mounting operation is improved.

  Next, the operation of the refrigerator according to the first embodiment will be described using the refrigerant circuit diagram of FIG. 3 and the Ph diagram of FIG. The alphabetical symbols in FIG. 3 and FIG. 6 and the text symbols indicate the same parts. The refrigerant compressed by the compressor 11 becomes a high-pressure and high-temperature (465 kPa, 60 ° C.) superheated vapor refrigerant and flows into the first condenser 13. It is cooled by air at room temperature (30 ° C.) by the blower 7 to dissipate heat, and is cooled to a high-pressure (465 kPa, 35 ° C.) relatively dry two-phase refrigerant. Then, as a result of dissipating heat to the outside of the refrigerator through the side pipe that is the second condenser 14, the refrigerant is condensed and liquefied in the pipe around the door that is the third condenser 15, and the dryness is low. It becomes a two-phase refrigerant. After that, the pressure is reduced by the capillary 16 which is a throttle means, and a low-pressure low-temperature (46 kPa, −30 ° C.) two-phase refrigerant flows into the cooler 17. In the cooler 17, the low-pressure and low-temperature two-phase refrigerant evaporates and cools the air in the refrigerator. The low-pressure and low-temperature vapor refrigerant flows into the compressor 11, is compressed again, and flows into the first condenser 13 as high-temperature and high-pressure superheated vapor refrigerant.

  A heat insulating structure is incorporated in the housing of the refrigerator, and the second condenser 14 and the third condenser are embedded in the heat insulating structure around the side of the refrigerator or around the door. It becomes the heat load of the refrigerator. On the other hand, the machine room 6 provided in the lower back surface of the refrigerator is located outside the heat insulating structure. For this reason, the heat radiation from the first condenser 13 disposed in the machine room 6 is released to the outside, and no heat is applied to the refrigerator cabinet. Therefore, more heat radiation with the first condenser leads to a reduction in the heat load of the refrigerator.

  In the first embodiment, compared to a conventional fin-and-tube heat exchanger (heat transfer tube diameter 6.35 mm, row number 6 rows, row number 2 rows, fin pitch 5 mm, step pitch 25.4 mm, row pitch 22 mm) The first condenser (heat transfer tube long side 16 mm, short side 2 mm, number of rows 3 rows, number of steps 14 steps, step pitch 8 mm, row pitch 16 mm) has about twice the heat transfer performance (heat transfer rate [W / m2K]). FIG. 7 shows the result of measuring the heat transfer coefficient outside the tube with respect to the front wind speed. Moreover, the result of having measured the ventilation pressure loss of the 1st condenser 13 is shown in FIG. From the figure, it can be seen that the ventilation pressure loss of the first condenser 13 is about 0.5 times that of the conventional fin-and-tube heat exchanger.

  For example, when heat is exchanged between air at 30 ° C. and R600a (isobutane) at a condensing temperature of 35 ° C., a conventional fin-and-tube heat exchanger (heat transfer tube diameter 6.35 mm, 6 rows, 2 rows) The heat resistance of the fin pitch 5 mm, step pitch 25.4 mm, row pitch 22 mm) is 0.59 K / W, whereas the first condenser 13 (heat transfer tube long side 16 mm, short side 2 mm, flow path The thermal resistance in the tube having the number 12, the number of rows 3, the number of steps 14, the step pitch 8 mm, and the row pitch 16 mm is 0.04 K / W. That is, the thermal resistance of the first condenser 13 is 1/10 or less of the thermal resistance of the conventional fin-and-tube heat exchanger. Thus, the heat exchange efficiency can be improved by the effect of expanding the heat transfer area in the flat heat transfer tube 21 by the plurality of refrigerant flow paths.

As described above, if the first condenser 13 according to the first embodiment is used, the heat exchange capacity is increased as compared with the conventional fin-and-tube type condenser, and thus the second condenser 14 and the third condenser 13 are used. This makes it possible to reduce the size of the condenser 15 and to reduce the amount of refrigerant.
Moreover, if the 1st condenser 13 is used and the 2nd condenser 14 and the 3rd condenser 15 are used as it is, the performance of the whole condenser will improve and the effect of reducing the power consumption of a refrigerator will also be acquired. It is done.
Furthermore, since the 1st condenser 13 is comprised only with the flat heat exchanger tube 21, manufacture becomes easy and it becomes possible to supply a low-cost refrigerator-freezer.

  Here, the flat heat transfer tube 21 is concerned about the pressure loss of the refrigerant in the refrigerant flow path formed therein. However, the amount of R600a (isobutane) filled in the refrigeration cycle of the refrigerator is small and the circulation rate is small, so that the pressure loss inside the flat heat transfer tube 21 is small. For this reason, when the 1st condenser 13 is used for the refrigerating cycle of a refrigerator, it is effective especially for the improvement of the heat exchange efficiency of a condenser.

  FIG. 9 is a perspective view showing a method of fixing the first condenser 13. The first condenser 13 is composed of three rows, the first row and the second row are offset by 0.5 stage vertically upward, and the third row is also 0.5 stage perpendicular to the second row. The state is offset downward. In order to maintain this state, fixing members 25 are arranged at both ends of the first condenser. The fixing member 25 has a comb-like shape, and is inserted into the gap so that the first row and the third row can be fixed at the same height and the second row can be fixed vertically downward by 0.5 steps. Since the first condenser 13 is formed by bending the flat heat transfer tube 21 in a meandering manner, it has a spring property and easily vibrates up and down. Therefore, the vibration of the flat heat transfer tube 21 can be easily and reliably suppressed by inserting and fixing the fixing member 25 into the flat heat transfer tube 21. Further, since only the fixing member 25 needs to be inserted, the manufacturing is easy and the number of parts can be reduced. Furthermore, since the fixing member 25 has a comb-teeth shape, it can be inserted and fixed in a plurality of gaps at the same time, thereby improving manufacturing efficiency.

The shape of the fixing member 25 is not limited to the shape shown in FIG. 9 and may be a shape as shown in FIG.
10A and 10B are diagrams showing another example of the fixing member 25. FIG. 10A is a perspective view of the fixing member 25 assembled, and FIG. 10B is an exploded view of the fixing member 25. FIG. The front view of a state is shown. The fixing member 25 has a frame shape in which crosspieces 25a are formed at predetermined intervals in the longitudinal direction (vertical direction in FIG. 10), and includes fixing members 26 and 27. The fixing member 26 has a comb-like shape in which convex portions 26a and concave portions 26b are alternately formed. An engaging protrusion 26c is formed at the tip of the convex portion 26a, and an engaging concave portion 26d is formed at a substantially central portion of the bottom of the concave portion 26b. The fixing member 27 also has a comb-like shape in which convex portions 27a and concave portions 27b are alternately formed. An engaging protrusion 27c is formed at the tip of the convex portion 27a, and an engaging concave portion 27d is formed at a substantially central portion of the bottom of the concave portion 27b.

  By engaging the engaging protrusion 26c of the fixing member 26 and the engaging recess 27d of the fixing member 27, and the engaging recess 26d of the fixing member 26 and the engaging protrusion 27c of the fixing member 27, respectively, the fixing member 26 and the fixing member 27 are engaged. Are joined together to form the fixing member 25. At this time, the convex portion 26a of the fixing member 26 and the convex portion 27a of the fixing member 27 become the crosspieces 25a. By inserting the bars 25a into the gaps of the stacked bodies 22a to 22c in the same manner as in FIG. 9, the vertical interval (gap) of the flat heat transfer tubes 21 forming the stacked bodies 22a to 22c can be maintained. . Furthermore, since the stacked bodies 22a to 22c can be fixed in the column direction by the bottom of the concave portion 26b of the fixing member 26 and the bottom of the concave portion 27b of the fixing member 27, it is possible to prevent the stacked bodies 22a to 22c from bulging in the column direction.

As described above, according to the first embodiment, a heat exchanger can be easily manufactured by simply bending the flat heat transfer tube 21 in a meandering manner, so that processing work for parts such as fins is not required, and the manufacturing cost is greatly increased. Can be reduced.
Moreover, since the air path 23 is formed in the whole gap | interval of the adjacent flat heat exchanger tube 21, the cross-sectional area of the air path 23 becomes large. As a result, the ventilation resistance is reduced, and the power of the blower 7 can be reduced.
Furthermore, since the air passage 23 is formed in the entire gap, the cross-sectional area of the air passage 23 is increased. As a result, foreign matters such as dust are not easily clogged, and heat transfer performance can be maintained for many years. In particular, heat transfer performance can be maintained for many years even when a heat exchanger is placed in a place (such as the machine room 6) where dust is likely to adhere, such as the lower back of the refrigerator. A high refrigerator can be supplied.

  Further, since the first condenser 13 forms the air passage 23 in the entire gap between the adjacent flat heat transfer tubes 21, the ventilation resistance is small, and R600a (isobutane), which is a flammable refrigerant, leaks into the machine chamber 6. Even if it is exhausted quickly. For this reason, a safer refrigerator can be provided to the user.

Moreover, since the 1st condenser 13 does not use the fin unlike the fin-and-tube type heat exchanger used conventionally, a shape can be changed arbitrarily. For example, it may be configured to be bent in a curved shape or wound in a circular shape. Furthermore, since fins are not used, it is possible to configure a highly reliable heat exchanger that is resistant to clogging of the air flow path due to adhesion of dust and the like.
Further, since the first condenser 13 is offset in the first and second rows, there is an effect of improving the heat transfer performance. Furthermore, since the 1st condenser 13 is being fixed with the fixing member 25, there exists an effect which maintains heat transfer performance and maintains a form. Furthermore, fixing to the refrigerator body is also easy.

  In addition, in this Embodiment 1, although demonstrated taking the refrigerator as an example, you may apply the heat exchanger of this Embodiment 1 to an air conditioner. In other words, the compressor 11, the first condenser 13, the capillary 16 as the throttle means and the cooler 17 are sequentially connected, and the first condenser 13 has a flat heat transfer tube 21 in a meandering shape. It is good also as an air-conditioning apparatus provided with the laminated body 22 which bent and provided the gap | interval and laminated | stacked, and the air path 23 formed in the whole gap | interval. And if it is such an air conditioner, the processing operation of parts, such as a fin, becomes unnecessary, the effect that a manufacturing cost can be reduced significantly, ventilation resistance becomes small, and the motive power reduction of the air blower 7 is attained. As a result, it is difficult to clog foreign matters such as dust and the like, and all of the operational effects that heat transfer performance can be maintained for many years are exhibited.

  In the first embodiment, R600a is used as the refrigerant. However, the present invention is not limited to this, and other natural refrigerants such as carbon dioxide as well as HFC refrigerants have the same effect. Furthermore, although aluminum (A1050) was used for the first condenser 13, it is not limited to this, and an aluminum alloy such as A3003 or A7072 may be used, and other metals such as copper and stainless steel may be used.

  In the first embodiment, aluminum is used for the connection member 24. However, the present invention is not limited to this, and various materials can be used similarly to the first condenser 13 (flat heat transfer tube 21). . For example, when the tubular pipe extending from the compressor 11 is made of copper, the connecting member 24 may be made of copper. In this case, the connection between the connecting member 24 and the flat heat transfer tube 21 is performed by brazing or bonding, for example.

  Further, the first condenser 13 may be formed by laminating the flat heat transfer tubes 21 in the left-right direction with respect to the ventilation direction (the first condenser 13 shown in FIG. Rotated state). That is, one flat heat transfer tube 21 is bent in a meandering manner in the left-right direction substantially perpendicular to the ventilation direction, and a plurality of flat heat transfer tubes 21 are stacked to form a first-layer stacked body 22a. At the end, the flat heat transfer tube 21 is bent and moved in the vertical direction (ventilation direction), and is bent again in the left-right direction substantially perpendicular to the ventilation direction, thereby stacking the flat heat transfer tubes 21 in a plurality of stages and stacking the second row. 22b is formed. Furthermore, it may be bent again in the vertical direction (ventilation direction) at the end, and laminated in the left-right direction substantially perpendicular to the ventilation direction of the multi-stage flat heat transfer tubes 21 to form a third-layer laminated body 22c.

  By forming the first condenser 13 in this way, the refrigerant flow path in the flat heat transfer tube 21 is formed in the vertical direction. For this reason, it becomes easy to form a liquid film of a refrigerant with good heat transfer on the inner wall surface of the refrigerant flow path in the flat heat transfer tube 21, and the heat transfer efficiency can be improved. Therefore, the heat exchange efficiency of the first condenser 13 is improved. Improve. Moreover, since dust collects in the bending part below the laminated body 22, dust clogging can also be suppressed.

  Moreover, as shown in FIG. 11, you may form the 1st condenser 13, bending the flat heat exchanger tube 21 into a waveform. Thereby, the effective heat transfer area outside the tube per unit volume can be expanded, and the heat exchange performance of the first condenser 13 is improved.

Embodiment 2. FIG.
In the first embodiment, in the machine room 6 of the refrigerator, the first condenser 13 is arranged on the leeward side of the blower 7, that is, on the blowout side of the blower 7. However, the arrangement is not limited to this, and the first condenser 13 may be arranged on the windward side of the blower 7, that is, on the suction side of the blower 7.
In the second embodiment, items not particularly described are the same as those in the first embodiment, and the same functions are described using the same reference numerals.

12A and 12B are diagrams showing the machine room 6 of the refrigerator according to the second embodiment, where FIG. 12A is a top view, and FIG. 12B is a rear view (showing the same direction as FIG. 2 in the first embodiment). Indicates.
Unlike the first embodiment, the first condenser 13 is arranged on the windward side of the blower 7, that is, on the suction side of the blower 7. The air flowing through the suction side of the blower 7 has a small difference between the speed of the air flowing through the blade periphery of the blower 7 and the speed of the air flowing through the center of the blower 7. Therefore, compared with the case where the 1st condenser 13 is arrange | positioned at the blowing side of the air blower 7, the velocity distribution of the air which flows through the air path 23 of the 1st condenser 13 becomes more uniform.

  Between the low-pressure accumulator 18 and the compressor 11, a pipe 28a through which low-pressure and low-temperature vapor refrigerant flows is connected. The pipe 28 a extends from the top surface side (upper side) of the refrigerator to the connection port 11 a of the compressor 11. Between the compressor 11 and the 1st condenser 13, the piping 28b through which the superheated steam refrigerant of a high pressure high temperature (465 kPa, 60 degreeC) distribute | circulates is connected. This pipe 28b passes from the connection port 11b of the compressor 11 to the blowout side of the blower 7 and between the blower 7 and the freezer compartment 5 to the connection port 13a (refrigerant inlet) of the first condenser 13. It is extended. Further, a pipe 28c through which a two-phase refrigerant having a relatively high dryness flows is connected between the first condenser 13 and the second condenser 14. The pipe 28c extends from the connection port 13b (refrigerant outlet) of the first condenser 13 to the top side of the refrigerator.

The first condenser 13 in the second embodiment is formed by a single flat heat transfer tube, and includes a first-row stacked body 22a and a second-row stacked body 22b. For this reason, by providing the connection port 13a on the top surface side of the stacked body 22a in the first row, the connection port 13b is provided on the top surface side of the stacked body 22b in the second row.
In addition, when the connection port 13a is provided in the bottom face side, the connection port 13b can be provided in the top | upper surface side by making the laminated body 22 into an odd number row.

In the refrigerator configured as described above, the first condenser 13 and the second condenser 14 are connected by providing the refrigerant outlet side connection port 13b of the first condenser 13 on the top surface side. Since the length of the pipe 28c can be shortened, the manufacturing cost of the refrigerator can be reduced.
Further, the pipe 28b connecting the compressor 11 and the first condenser 13 passes between the blowout side of the blower 7 and between the blower 7 and the freezer compartment 5, that is, the pipe 28b is the wind speed of the blower 7. It is provided in a large area. For this reason, the high-pressure and high-temperature (465 kPa, 60 ° C.) superheated vapor refrigerant flowing through the pipe 28b is cooled by the air sent from the blower 7, so that the heat exchange efficiency of the entire refrigeration cycle provided in the refrigerator is improved.

  Since the 1st condenser 13 is arrange | positioned at the suction side of the air blower 7, compared with the case where the 1st condenser 13 is arrange | positioned at the blowing side of the air blower 7, the air path 23 of the 1st condenser 13 is provided. The velocity distribution of the flowing air becomes more uniform. For this reason, the amount of heat exchange between the refrigerant and air increases, and the heat exchange efficiency of the first heat exchanger 13 is improved. Moreover, since the air with a large wind speed blown from the air blower 7 can be sent to the compressor 11, it becomes possible to cool the compressor 11, and compressor efficiency improves.

Embodiment 3 FIG.
In the first embodiment and the second embodiment, the first condenser 13 is formed by laminating one flat heat transfer tube 21 in the vertical direction or the horizontal direction. However, the present invention is not limited to this, and various forms are possible. . In Embodiment 3, items that are not particularly described are the same as those in Embodiment 1 or Embodiment 2, and the same functions are described using the same reference numerals.

  FIG. 13 is a perspective view showing an example of the first condenser 13 according to the third embodiment. A partition wall is provided at equal intervals in the flat heat transfer tube 21 and is partitioned into a plurality of refrigerant flow paths. The flat heat transfer tube 21 is bent into an oval shape and is wound inwardly to form a first row of spiral bodies 29a while providing a gap of a predetermined size. Part or all of this gap becomes the air passage 23. The flat heat transfer tube 21 bent into an oblong shape at the innermost peripheral portion is bent in the ventilation direction. And it is bent again in the shape of an ellipse, and it winds outwardly, providing the gap | interval of the predetermined magnitude | size used as the air path 23, and forms the 2nd row | line | column spiral body 29b. The flat heat transfer tubes 21 are wound around the second row of spiral bodies 29b at positions facing the gaps of the first row of spiral bodies 29a.

  The connection port 13a is provided on the top surface side of the first row of spiral bodies 29b. For this reason, the connection port 13b can be provided in the top | upper surface side by comprising the 1st condenser 13 by the spiral body 29 of an even number row | line | column. By providing the refrigerant outlet side connection port 13b in the first condenser 13 on the top surface side, the length of the pipe 28c connecting the first condenser 13 and the second condenser 14 can be shortened. The manufacturing cost of the refrigerator can be reduced. Moreover, since the speed of the air which flows through the wing | blade peripheral part of the air blower 7 is faster than the speed of the air which flows through the center part of the air blower 7, it connects with the refrigerant | coolant inflow piping 28b connected to the connection port 13a, and the connection port 13b. The heat exchange efficiency of the first condenser 13 can be improved by providing the refrigerant outflow pipe 28c in a range facing the blade periphery of the blower 7 having a high air speed.

  Since the spiral body 29 of the first condenser 13 configured in this way is bent more gently than the laminated body 22 in the first embodiment, the pressure loss of the refrigerant can be suppressed. Moreover, since the spiral body 29a and the spiral body 29b are each connected by the flat heat transfer tube 21 at the innermost peripheral portion, the structure of the first condenser 13 can be made compact.

  In addition, the bending shape of the flat heat exchanger tube 21 is not limited to an oblong shape, For example, you may be bent in circular shape. You may form the 1st condenser 13 using the flat heat exchanger tube 21 bent by the waveform. Further, the capacity of the first condenser 13 can be easily adjusted by increasing the number of turns of each spiral body or increasing the number of rows. For example, the spiral bodies 29 may be arranged in three rows. At this time, when the first and second row spiral bodies 29 are connected by the innermost flat heat transfer tube 21, the second row and third row spiral bodies 29 are respectively connected to the outermost flat heat transfer tubes. By connecting at 21, the structure of the first condenser 13 can be made compact.

  FIG. 14 shows another example of the first condenser 13 according to the third embodiment. The flat heat transfer tube 21 is bent into an oval shape and is wound inwardly while forming a first condenser 13 while providing a gap serving as an air passage 23. Moreover, the width of the gap provided between the flat heat transfer tubes, that is, the width of the air passage 23 is larger on the innermost peripheral side than on the outermost peripheral side. The speed of the air flowing through the blade periphery of the blower 7 is faster than the speed of the air flowing through the center of the blower 7. Therefore, heat exchange between air and the refrigerant is promoted by reducing the width of the air passage 23 in a range facing the blade peripheral portion of the blower 7 having a high air speed. Moreover, the speed reduction of the air which flows through the air path 23 can be suppressed by enlarging the width | variety of the air path 23 of the range facing the center part of the air blower 7 with slow air speed. Thus, the heat exchange efficiency of the first condenser 13 can be improved by changing the width of the air passage 23 corresponding to the speed of the air flowing through the air passage 23.

Alternatively, the first condenser 13 (heat exchanger) and the blower 7 may be unitized to form a condenser (heat exchanger) 130.
FIG. 15 shows an example of the condensing device 130 according to the third embodiment. FIG. 15 shows a side sectional view of the condensing device 130. The condensing device 130 includes a first condenser 13 and a blower. The first condenser 13 includes, for example, four rows of spiral bodies 29a to 29d. The spiral body 29 a and the spiral body 29 d are formed by winding the flat heat transfer tube 21 into a circular shape and winding it in a spiral shape with a gap of a predetermined size serving as the air passage 23. The spiral body 29b and the spiral body 29c have a shape wound only once, and are formed so as to cover the blower 7.
Note that the number of the spiral bodies 29 is not limited to four, and may be any number. Further, the number of turns of the spiral bodies 29a to 29d can be arbitrarily changed.

  The first condenser 13 is supplied with high-pressure and high-temperature superheated steam refrigerant from a connection port 13 a provided on the blow-out side of the blower 7, and has a relatively high dryness from the connection port 13 b provided on the suction side of the blower 7. Two-phase refrigerant flows out. That is, the refrigerant flow of the first condenser 13 and the air flow of the air passage 23 are counterflows.

  FIG. 16 is a characteristic diagram showing the relationship between the temperature change of the refrigerant flowing through the first condenser 13 and the temperature change of the air flowing through the air passage 23. The 50 ° C. high-pressure and high-temperature superheated vapor refrigerant flowing into the first condenser 13 from the connection port 13a is cooled by exchanging heat with the air flowing through the air passage 23 to become a 33 ° C. two-phase refrigerant. Thereafter, the two-phase refrigerant exchanges heat with the air flowing through the air passage 23 and becomes a two-phase refrigerant having a relatively high dryness, and flows out of the first condenser 13 (during this time, the isothermal change occurs and the refrigerant temperature Is 33 ° C.).

When the refrigerant flow of the first condenser 13 and the air flow of the air passage 23 are parallel flows, the 30 ° C. air flowing into the air passage 23 exchanges heat with the refrigerant flowing through the first condenser 13 and is heated. Then the temperature rises. However, there is no temperature difference with the refrigerant as it flows downstream, and heat exchange cannot be performed.
On the other hand, when the refrigerant flow of the first condenser 13 and the air flow of the air passage 23 are counterflows, the 30 ° C. air flowing into the air passage 23 exchanges heat with the refrigerant flowing through the first condenser 13. It is heated and the temperature rises. As this air flows downstream, it exchanges heat with a refrigerant having a high temperature, so that a temperature difference with the refrigerant is ensured until it flows out of the air passage 23 and heat exchange can be performed.

  In the condensing device 130 configured in this manner, the refrigerant flow of the first condenser 13 and the air flow of the air passage 23 are opposed to each other, so that the heat exchange efficiency is improved. Moreover, since the 1st condenser 13 is provided so that the air blower 7 may be covered, since it can exchange heat with air with a large wind speed, heat exchange efficiency improves further. Moreover, since the 1st condenser 13 functions also as a duct, it becomes unnecessary to provide a duct and it becomes possible to reduce cost.

  FIG. 17 shows still another example of the condensing device 130 according to the third embodiment. FIG. 17 shows a side sectional view of the condensing device 130. The condensing device 130 includes a first condenser 13 and a blower. The first condenser 13 includes, for example, nine rows of spiral bodies 29a to 29i. The spiral bodies 29a to 29c and the spiral bodies 29f to 29i are formed such that the flat heat transfer tube 21 is bent into, for example, a circular shape and is spirally wound with a gap of a predetermined size serving as an air passage 23a. . The spiral body 29d and the spiral body 29e have a shape wound only once, and are formed so as to cover the blower 7.

  In the spiral bodies 29 a to 29 d, the diameter of the flat heat transfer tube 21 at the innermost peripheral portion in each spiral body decreases as the distance from the blower 7 increases. The diameters of the flat heat transfer tubes 21 at the innermost peripheral portions of the spiral bodies 29e to 29i also become smaller as the distance from the blower 7 increases. That is, an air passage 23 b that extends from the windward side of the blower 7 to the blower 7 and contracts from the blower 7 to the leeward side of the blower 7 is formed inside the first condenser 13. Further, in the spiral bodies 29a to 29c, the flat heat transfer tube 21 is wound in a range facing the air passage 23 of the adjacent spiral bodies (for example, the spiral bodies 29a and 29c in the spiral body 29b). The flat heat transfer tubes 21 are wound around the spiral bodies 29f to 29i at positions facing the air paths 23 of the adjacent spiral bodies.

  In the condensing device 130 configured as described above, since the air passage 23b in which the air passage changes smoothly is formed inside the first condenser 13, the first condenser 13 (the air passage 23) is provided. Ventilation resistance of flowing air is reduced. In addition, since the air passage 23b extends from the windward side of the blower 7 to the blower 7 and contracts from the blower 7 to the leeward side of the blower 7, the change in wind speed is reduced, and the first condenser 13 is reduced. The heat transfer efficiency is improved. Moreover, since the 1st condenser 13 is provided so that the air blower 7 may be covered, it becomes unnecessary to provide a duct and it becomes possible to reduce cost. Furthermore, since the 1st condenser 13 is provided so that the air blower 7 may be covered, the noise of the air blower 7 can be reduced.

  Note that the number of columns of the first condenser 13 is not limited to nine, and may be any number. The number of turns of the spiral bodies 29a to 29i can also be arbitrarily changed. For example, the first condenser may be formed by winding the flat heat transfer tube 21 spirally with one turn.

  FIG. 18 shows still another example of the condensing device 130 according to the third embodiment. FIG. 18 shows a perspective view of the condensing device 130. The condensing device 130 includes the first condenser 13 and a blower. The first condenser 13 is formed by winding a flat heat transfer tube 21 into, for example, a circular shape and winding it in a spiral shape with a gap of a predetermined size serving as an air passage 23. Further, the diameter d2 (minimum winding diameter) of the flat inner heat transfer tube 21 is larger than the diameter d1 of the fan motor 7a provided in the blower 7.

  The first condenser 13 and the flat heat transfer tube 21 are arranged so that the fan motor 7a is inserted into a space having a diameter d2 formed inside the innermost peripheral portion. Note that the first condenser 13 may be formed by winding the flat heat transfer tube 21 around the fan motor 7a. Further, a comb-like fixing member 25 is inserted into the gap between the spiral bodies 29 constituting the first condenser 13, and this fixing member 25 is fixed to the base 25b. The fan motor 7a is fixed to the fixing member 25, and the fixing member 25 also has a function as a motor base. That is, the blower 7, the fan motor 7a, and the first condenser 13 are integrally formed.

  In the condensing device 130 configured in this way, the first condenser 13 exchanges heat only with the air in the vicinity of the blade periphery of the blower 7 having a high wind speed, so that the heat exchange efficiency is improved. Since the flat heat transfer tube 21 is not wound in a range facing the fan motor 7a having a low wind speed, the cost can be reduced by the length of the flat heat transfer tube 21. Further, the occupied volume of the first condenser 13 and the blower 7 in the machine room 6 can be made compact. Further, since the first condenser 13 covers the fan motor 7a, the noise of the fan motor 7a can be reduced. Further, since the fan motor 7a closes the space having the diameter d2 formed inside the innermost peripheral portion of the flat heat transfer tube 21, the diameter d2 formed inside the innermost peripheral portion of the flat heat transfer tube 21 is closed. The air flow sucked into the blower 7 through the space is eliminated, and the heat exchange efficiency of the first condenser 13 is improved. Further, since the fixing member 25 also functions as a motor support, it is not necessary to provide a motor support separately, and it is possible to reduce the size and cost.

  FIG. 19 shows still another example of the first condenser 13 according to the third embodiment. FIG. 19 shows a side view of the first condenser 13. The first condenser 13 is composed of, for example, four rows of spiral bodies 29a to 29d. These spiral bodies 29 a to 29 d are formed by winding the flat heat transfer tube 21 into, for example, a circular shape and winding it in a spiral shape with a gap of a predetermined size serving as the air passage 23. Further, the spiral bodies 29 a to 29 d are formed by separate flat heat transfer tubes 21. These spiral bodies 29a to 29d are connected by a header 30 (common pipe) provided in a space formed inside the innermost peripheral portion of each flat heat transfer tube 21.

  In the first condenser 13 configured in this manner, the spiral bodies 29a to 29d are each formed by separate flat heat transfer tubes 21, that is, since the refrigerant flow path is short, the pressure loss of the refrigerant is reduced. can do. Moreover, since the header 30 closes the space formed inside the innermost peripheral portion of the flat heat transfer tube 21, the heat exchange efficiency of the first condenser 13 is improved.

It is a front view which shows the refrigerator which concerns on this Embodiment 1. FIG. It is a rear view which shows the state which removed the machine room cover of the refrigerator which concerns on this Embodiment 1. FIG. It is a circuit diagram which shows the structure of the refrigerant circuit of the refrigerator which concerns on this Embodiment 1. 3 is a perspective view showing a detailed structure of a first condenser 13 according to Embodiment 1. FIG. It is a perspective view which shows schematic structure of the connection member 24 which concerns on this Embodiment 1. FIG. It is a Ph diagram showing the operation of the refrigeration cycle according to the first embodiment. It is a graph which shows the heat transfer coefficient outside the tube of the 1st condenser 13 concerning this Embodiment 1. FIG. It is a graph which shows the ventilation pressure loss of the 1st condenser 13 which concerns on this Embodiment 1. FIG. It is a perspective view which shows the fixing method of the 1st condenser 13 which concerns on this Embodiment 1. FIG. It is a figure which shows another example of the fixing member 25 which concerns on this Embodiment 1. FIG. It is a perspective view which shows another example of the 1st condenser 13 which concerns on this Embodiment 1. FIG. It is a figure which shows the machine room 6 of the refrigerator which concerns on this Embodiment 2, (a) is a top view, (b) is a rear view (The figure which shows the same direction as FIG. 2 in Embodiment 1). It is a perspective view which shows an example of the 1st condenser 13 which concerns on this Embodiment 3. FIG. It is a front view which shows another example of the 1st condenser 13 which concerns on this Embodiment 3. FIG. It is side surface sectional drawing which shows an example of the condensing apparatus 130 which concerns on this Embodiment 3. FIG. 6 is a characteristic diagram showing the relationship between the temperature change of the refrigerant flowing through the first condenser 13 and the temperature change of the air flowing through the air passage 23. It is side surface sectional drawing which shows another example of the condensing apparatus 130 which concerns on this Embodiment 3. It is a perspective view which shows another example of the condensing apparatus 130 which concerns on this Embodiment 3. FIG. It is a perspective view which shows another example of the 1st condenser 13 which concerns on this Embodiment 3. FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Refrigerator room, 2 ice making room, 3 switching room, 4 vegetable room, 5 freezer room, 6 machine room, 7 air blower, 7a fan motor, 11 compressor, 11a, b connection port, 13 1st condenser, 13a, b connection port, 14 second condenser, 15 third condenser, 16 capillary tube, 17 cooler, 18 low pressure accumulator, 21 flat heat transfer tube, 22 (22a-22c) laminate, 23 (23a, b) wind Road, 24 connecting member, 25 fixing member, 25a crosspiece, 25b base, 26 fixing member, 26a convex portion, 26b concave portion, 26c engaging projection, 26d engaging concave portion, 27 fixing member, 27a convex portion, 27b concave portion, 27c Joint protrusion, 27d engaging recess, 28a, b, c piping, 29 (29a-29i) spiral, 30 header, 130 condenser.

Claims (23)

A laminated body in which a flat heat transfer tube is bent in a meandering manner and provided with a gap, and an air passage formed in the whole gap;
A plurality of the laminates are arranged in the ventilation direction,
A pair of adjacent laminates is
One bent side of one of the laminates and the other bent side of the other laminate are connected by the flat heat transfer tube,
A heat exchanger characterized in that a flat heat transfer tube portion of one of the laminates and a gap portion of the other laminate are arranged to face each other.   The heat exchanger according to claim 1, wherein the flat heat transfer tube is bent in a vertical direction perpendicular to a ventilation direction, and the flat heat transfer tubes are stacked in a horizontal direction. A spiral body in which a single flat heat transfer tube is spirally wound while providing a gap, and an air passage formed by the gap,
A plurality of the spiral bodies are arranged in the ventilation direction,
A pair of adjacent spirals is
The innermost peripheral part of the flat heat transfer tube in the mutual spiral body, or the outermost peripheral part of the flat heat transfer tube in the mutual spiral body is connected by the flat heat transfer tube,
A heat exchanger characterized in that a flat heat transfer tube portion of one of the spiral bodies and a gap portion of the other spiral body are arranged to face each other. The diameter of the innermost peripheral portion of the flat heat transfer tube in the spiral body is
4. The heat exchanger according to claim 3, wherein the heat exchanger is larger than a fan motor diameter of the blower. The gap is
The heat exchanger according to claim 3 or 4, wherein a gap on the innermost peripheral portion side of the spiral body is larger than a gap on the outermost peripheral portion of the spiral body.   The heat exchanger according to any one of claims 1 to 5, wherein the flat heat transfer tube is bent into a corrugated shape.   The heat exchanger according to any one of claims 1 to 6, further comprising a fixing member that is inserted into the gap and maintains a distance between the flat heat transfer tubes.   The heat exchanger according to claim 7, wherein the fixing member is a comb-like member inserted into the plurality of gaps.   The heat exchanger according to claim 7, wherein the fixing member is a frame-like member in which bars for insertion into the plurality of gaps are formed.   The heat exchanger according to any one of claims 1 to 9, wherein a connecting member having one flat end and a circular tubular end is provided at an end of the flat heat transfer tube. .   A heat exchange apparatus, wherein the fan motor of the blower and the heat exchanger according to any one of claims 4 to 6 are integrally formed.   A heat exchanger, wherein the blower is covered by part or all of the row of the spiral bodies in the heat exchanger according to any one of claims 3 to 6. The diameter of the innermost peripheral portion of the flat heat transfer tube in the spiral body is
The heat exchange device according to claim 12, wherein the diameter of the heat exchanger is increased from the windward side of the blower to the blower, and the diameter is reduced from the blower to the leeward side of the blower.   The heat exchange device according to any one of claims 11 to 13, further comprising a fixing member that is inserted into the gap and maintains a distance between the flat heat transfer tubes.   The heat exchanger according to claim 14, wherein the fixing member is a comb-like member inserted into the plurality of gaps.   The heat exchanger according to claim 14, wherein the fixing member is a frame-like member in which a plurality of bars for insertion into the plurality of gaps are formed.   The heat exchange device according to any one of claims 11 to 16, wherein a connecting member having one end flat and the other end circular is provided at an end of the flat heat transfer tube. . It has a refrigeration cycle in which a compressor, a condenser, a throttle means and a cooler are connected in sequence,
A refrigerator using the heat exchanger according to any one of claims 1 to 10 as the condenser. The refrigerator further includes a blower,
The refrigerator according to claim 18, wherein the condenser, the blower, and the compressor are arranged in this order from the windward side in the ventilation direction of the blower. It has a refrigeration cycle in which a compressor, a condenser, a throttle means and a cooler are connected in sequence,
A refrigerator using the heat exchange device according to any one of claims 11 to 17 as the condenser.   21. The refrigerator according to any one of claims 18 to 20, wherein the refrigerant used in the refrigeration cycle is natural refrigerant R600a (isobutane).   A refrigeration cycle in which a compressor, a condenser, a throttle means, and a cooler are sequentially connected, and the heat exchanger according to any one of claims 1 to 10 is used for the condenser. An air conditioner characterized by.   A refrigeration cycle in which a compressor, a condenser, a throttle means and a cooler are sequentially connected is provided, and the heat exchange device according to any one of claims 11 to 17 is used for the condenser. Air conditioner.

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